EP1884674A1 - Couplage élastique - Google Patents

Couplage élastique Download PDF

Info

Publication number
EP1884674A1
EP1884674A1 EP07005537A EP07005537A EP1884674A1 EP 1884674 A1 EP1884674 A1 EP 1884674A1 EP 07005537 A EP07005537 A EP 07005537A EP 07005537 A EP07005537 A EP 07005537A EP 1884674 A1 EP1884674 A1 EP 1884674A1
Authority
EP
European Patent Office
Prior art keywords
coupling
guide
bearing
rubber disc
guide bearing
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
EP07005537A
Other languages
German (de)
English (en)
Other versions
EP1884674B1 (fr
Inventor
Robert Peters
Andre Jansen
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Siemens AG
Original Assignee
A Friedrich Flender AG
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by A Friedrich Flender AG filed Critical A Friedrich Flender AG
Publication of EP1884674A1 publication Critical patent/EP1884674A1/fr
Application granted granted Critical
Publication of EP1884674B1 publication Critical patent/EP1884674B1/fr
Not-in-force legal-status Critical Current
Anticipated expiration legal-status Critical

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Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members
    • F16D3/76—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members shaped as an elastic ring centered on the axis, surrounding a portion of one coupling part and surrounded by a sleeve of the other coupling part
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D3/00—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive
    • F16D3/50—Yielding couplings, i.e. with means permitting movement between the connected parts during the drive with the coupling parts connected by one or more intermediate members

Definitions

  • the invention relates to a flexible coupling with the features of the preamble of claim 1.
  • Such highly elastic, containing a rubber disc element couplings are particularly suitable for coupling machines with a highly non-uniform torque curve or the occurrence of a large radial, axial or angular misalignment of the coupling halves.
  • rubber disc clutches are known in which between an inner and outer metallic ring anvulkaniserte on the cylindrical surfaces Gummiringusion is inserted.
  • the inner and outer metal rings in turn are each part of two halves of a clutch and connect in a shaft train the drive and the output shaft.
  • the vibration characteristics can be adjusted by the size of the rubber disc and the hardness of the rubber material.
  • the power flow in the drive train is always interrupted when the rubber disc between the inner and outer ring of the Coupling due to material failure by z. B. aging or overload is destroyed. In that case, the clutch will break and disconnect the drive from the output. Such a break is not a problem if the rigidly mounted machine parts have stored waves.
  • a disadvantage is an interruption, for example, in the use of a conventional highly elastic rubber disc clutch in vehicles.
  • the rotary motion is tapped on the shaft of a pair of wheels for driving a generator for generating electrical energy for the electrical system, increases the speed in a transmission and guided by means of a propeller shaft over greater distances to a generator.
  • a highly elastic rubber disc clutch suppresses unwanted nonuniformities from the drive as Vorschaltelement.
  • the gearbox and generator are mounted at different locations on the vehicle or bogie. Since the individual components of the vehicle are mutually displaceable and resiliently suspended to increase the ride comfort and to cushion the vibration excitation from the tracks, there is always a relative displacement of the drive components to each other. In normal operation, a cardan shaft compensates for this displacement. As soon as the highly elastic rubber coupling fails, however, a particularly critical operating state occurs. The break-through clutch is no longer able to guide the PTO shaft and will lead to collisions of machine parts in uncontrolled movements and thus possibly cause serious accidents.
  • a known in stationary drives overload protection by a separable cam teeth between the rubber washer and the internally toothed outer ring of the second coupling half is not possible due to the poor performance even in a version with a plain bearing support for emergency in mobile systems for safety reasons.
  • the rubber disc element is designed so that it is destroyed as the weakest link in the chain at excessive load. Such a measure is subject to a high degree of uncertainty and does not lead to the desired result. Instead, at high overload peaks tears the union of the PTO shaft on the clutch housing.
  • the invention has for its object to make the generic elastic coupling so that after a failure of the rubber disc element damage to or by the coupled machine parts with simple means and safely avoided.
  • the elastic coupling according to the invention is provided for emergency with a rotatable roller bearing, which leads to a defined leadership of the coupling halves to each other in case of failure of the rubber disc element.
  • the storage allows the integration of a simple and reliable mechanical overload protection in the highly elastic coupling.
  • a highly elastic coupling 1 is connected on one side via a propeller shaft 2 with a drive, not shown, and on the other side with a generator 9 as a driven machine.
  • the said machine parts are arranged on a vehicle.
  • the highly elastic, designed as a rubber disc clutch coupling 1 consists of a first coupling half 5 and a second coupling half 7.
  • a propeller shaft 2 has a flange 3, which is connected via stud bolts 4 with the first coupling half 5.
  • the second coupling half 7 is seated on a tapered shaft 8 a connected machine, z. B. a generator 9.
  • a rubber disc member 6 is provided in the form of a radially extending, annular disc made of an elastic material.
  • the propeller shaft 2 initiates the rotational movement via the flange 3 into the first coupling half 5.
  • the rubber disc element 6 transmits the rotational movement to the second coupling half 7.
  • the rubber disc member 6 is vulcanized to an inner ring 10 of the second coupling half 7.
  • the ring 10 is seated on a cylindrical surface 11 of the second coupling half 7.
  • the inner ring 10 and the cylindrical surface 11 of the second coupling half 7 are tolerated with a slight interference fit and form a frictional connection.
  • a positive locking element 12 is inserted between the inner ring 10 and the cylindrical surface 11 of the second coupling half 7 and prevents relative movement between the two parts.
  • a cam toothing 13 is introduced in the rubber material, which engages in an accurately fitting internal toothing 14 of an outer ring 15 of the first coupling half 5 (FIG. 2).
  • the outer ring 15 is frictionally and positively connected in a cylindrical bore 16 with the first coupling half 5.
  • the toothed transition from the cam teeth 13 of the rubber disc member 6 in the internal teeth 14 of the outer ring 15 forms a simple mechanical overload protection, which represents a novel solution in connection with the clutch 1 and its emergency running properties for mobile applications.
  • the cam teeth is a reliable overload protection that makes the design of the rubber disk element 6 as a predetermined breaking point superfluous. A larger dimensioning of the rubber disc element 6 even leads to a significant increase in the service life of the clutch 1. Another advantage of this design is the easier plug-in assembly.
  • the first coupling half 5 encloses a cup-shaped housing 17, the inner, second coupling half 7 and the between the Coupling halves 5, 7 inserted rubber disc element 6 and the guide bearings 18 and 19 described in more detail below.
  • the housing 17 representing the first coupling half 5 advantageously encloses the coupling 1 and forms a narrow gap to the front side of the generator 9. This design protects the rubber disk element 6 in comparison to known solutions against damage caused by stones whirled up or stirred up other debris and adverse weather conditions.
  • the front side can be screwed to the housing 17, the propeller shaft 6.
  • a plurality of threaded bores 20 are arranged around the rotational axis of the coupling 1 in the housing 17. The threaded bores 20 receive the stud bolts 4 and make the connection with the propeller shaft 2 ago.
  • a guide bearing arrangement is provided between the two coupling halves 5, 7, which advantageously consists of two guide bearings 18, 19.
  • the guide bearings 18 and 19 are designed as rolling bearings.
  • the bearings support in the highly elastic coupling 1 only in case of failure of the rubber disc member 6, the first coupling half 5 on the second coupling half 7 rotatably from.
  • a sufficiently large bearing clearance reduces the friction losses to a negligible proportion in normal operation and does not restrict the function of the highly elastic coupling 1 provided with a rubber disk element with a view to compensating for a large radial, axial or angular misalignment.
  • the guide bearing assembly with the two guide bearings 18, 19 thereby exercises the function of emergency storage.
  • the guide bearing assembly should have a radial bearing clearance which is just greater than the predetermined by the hardness and the size of the rubber disc element 6 offset of the propeller shaft 2 with respect to the shaft journal 8 of the generator.
  • the second coupling half 7 is seated on the conical shaft 8 of a working machine, for. As the generator 9, and is secured by an end plate 21. Since the guide bearings 18, 19 can not transmit any circumferential forces due to their design and arrangement, the Generator 9 is not further driven at interrupted power flow on serving as a coupling element rubber disc element 6 and stops.
  • the guide bearings 18, 19 are designed as life-sealed sealed bearings.
  • a shaft seal 22 and a washer 23 protect the guide bearings 18 and 19 from ingress of dirt.
  • the guide bearings 18, 19 can be designed as a simple deep groove ball bearings or advantageously as angular contact ball bearings.
  • angular contact ball bearings are suitable in an O arrangement to compensate for tilting moments from the attack of the weight of the propeller shaft 2.
  • the guide bearings 18, 19 are arranged on different lateral surfaces with different diameters and are axially offset close to each other.
  • the inner diameter of the guide bearing 18 is greater than the outer diameter of the guide bearing 19.
  • the inner ring of the guide bearing 18 is arranged on a cylindrical lateral surface 24 on the circumference of a radial web 25 of the second coupling half 7.
  • the increased support distance (O arrangement the angular contact ball bearing) between the guide bearings 18, 19 makes it possible to keep the axial distance between the guide bearings 18, 19 by means of the bearing arrangement on the lateral surface 24 of the radial web 25 very short. Due to the different bearing sizes, the Axialkraftanteile the guide bearings 18, 19 do not cancel. To apply the required difference, plate springs 26 generate an axial preload.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Mechanical Operated Clutches (AREA)
  • Dowels (AREA)
  • Control Of Motors That Do Not Use Commutators (AREA)
  • Pens And Brushes (AREA)
  • Rolls And Other Rotary Bodies (AREA)
  • Transmission Devices (AREA)
EP07005537A 2006-07-25 2007-03-17 Couplage élastique Not-in-force EP1884674B1 (fr)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
DE102006034892A DE102006034892A1 (de) 2006-07-25 2006-07-25 Elastische Kupplung

Publications (2)

Publication Number Publication Date
EP1884674A1 true EP1884674A1 (fr) 2008-02-06
EP1884674B1 EP1884674B1 (fr) 2011-01-26

Family

ID=38611103

Family Applications (1)

Application Number Title Priority Date Filing Date
EP07005537A Not-in-force EP1884674B1 (fr) 2006-07-25 2007-03-17 Couplage élastique

Country Status (5)

Country Link
EP (1) EP1884674B1 (fr)
AT (1) ATE497113T1 (fr)
DE (2) DE102006034892A1 (fr)
EA (1) EA010559B1 (fr)
ES (1) ES2359164T3 (fr)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
RU183656U1 (ru) * 2018-06-15 2018-09-28 Общество с ограниченной ответственностью "Центр инновационного развития СТМ" (ООО "ЦИР СТМ") Муфта комбинированная
US20240018858A1 (en) * 2022-07-12 2024-01-18 Caterpillar Inc. Electric fracturing drivetrain

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1733771A (en) 1928-01-21 1929-10-29 Trinity Wheel Corp Flexible driving mechanism
DE3545027A1 (de) * 1985-12-19 1987-06-25 Hackforth Gmbh & Co Kg Elastische wellenkupplung
DE8912387U1 (de) 1989-10-18 1990-01-04 MAGNA INTERNATIONAL GmbH, 6460 Gelnhausen Torsionsschwingungsgedämpfte Riemenscheibe
EP0462356A1 (fr) * 1990-06-09 1991-12-27 Firma Carl Freudenberg Accouplement élastique rotatif

Family Cites Families (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE884715C (de) * 1951-06-29 1953-07-30 Stromag Maschf Kupplung zur UEbertragung grosser Drehmomente
GB837659A (en) * 1957-03-07 1960-06-15 Maybach Motorenbau Gmbh Improvements in or relating to torque-transmitting mechanical couplings
DE1822342U (de) * 1957-03-07 1960-11-24 Maybach Motorenbau Gmbh Kupplung.
DE3430298A1 (de) * 1984-08-17 1986-02-27 Goetze Ag, 5093 Burscheid Schwingungsdaempfende riemenscheibe
DE3528175A1 (de) * 1985-08-06 1987-02-19 Freudenberg Carl Fa Schwungrad
SE515062C2 (sv) * 1999-10-29 2001-06-05 Falk Ab Curt Vridmomentbegränsande kopplingsanordning

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1733771A (en) 1928-01-21 1929-10-29 Trinity Wheel Corp Flexible driving mechanism
DE3545027A1 (de) * 1985-12-19 1987-06-25 Hackforth Gmbh & Co Kg Elastische wellenkupplung
DE8912387U1 (de) 1989-10-18 1990-01-04 MAGNA INTERNATIONAL GmbH, 6460 Gelnhausen Torsionsschwingungsgedämpfte Riemenscheibe
EP0462356A1 (fr) * 1990-06-09 1991-12-27 Firma Carl Freudenberg Accouplement élastique rotatif

Also Published As

Publication number Publication date
DE102006034892A1 (de) 2008-01-31
EA010559B1 (ru) 2008-10-30
EA200701011A1 (ru) 2008-02-28
ES2359164T3 (es) 2011-05-19
ATE497113T1 (de) 2011-02-15
EP1884674B1 (fr) 2011-01-26
DE502007006349D1 (de) 2011-03-10

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